Liquid transmission device



5am, 23, H945. F, w GUlBER-r ET AL 2,368,019

LIQUID TRANSMISSION DEVICE Filedoct. 13, 1941 2 sheets-*sheet 1 ATTORNEY jan 23 w45. F. w. GUIBERT ET AL. 2,368,019

LIQUID TRANSMISSION DEVICE Filed Oct. 15. 1941 2 Sheets-Sheet 2 INVE'NTO RS @Y www Y ATTQRN EY Patented Jan. 23, 1945 2,368,019' LIQUID TRANSMISSION DEVICE Francis W. Guibert, Los Angeles, and Frederic B. Fuller. Whittier, Calif.; said Fuller assignor to said Guibert Application October 13, 1941, Serial No. 414,704

6 Claims.

This invention relates to a liquid flow device, capable of being driven by flow of liquid, as for measurement of the flow, or of operating as a' pump upon a liquid;

Liquid flow meters of various types have been devised. In one form, a casing is provided having two rotors of general elliptical form, rotatable about their geometric centers and having intermeshing teeth. The casing has an inlet and an outlet, and its walls are of circular cylindrical form, capable of being in sealing contact with the rotors at the points of maximum radius of the rotors in the course of rotation thereof. In this way, liquid is periodically permitted to enter into the spaces between the rotors and the casing walls; the liquid is subsequently trapped and later discharged'as the rotors continue their angular movement.

It is readily demonstrable that if the rotors have pitch lines 'conforming exactly to true 1el lipses, then the pitch lines do not continue, to touch each other throughout a. complete revolution; instead, they are separated at places corresponding to a portion of the pitch arc intermediate the major and minor axes. It -is possible to modify the form .of the elliptic lobes to. overcome this discrepancy; but further considerations readily show that a random mode of compensation is not satisfactory.

In arriving at a satisfactory solution, certain conditions of operation of the metering function must be considered. The liquid being measured is to iiow out of the meter with as little pulsation as possible. It may be assumed that the liquid prior to the time it reaches the meter has a substantially steady flow. Obviously, if one of the' 'two rotors be driven at a uniform angular rate,

the rate of rotation of the .other rotor cyclically varies from a minimum to a'maximum throughout each quarter revolution. This is a necessary.

result of the fact that theradius of the driving rotor drawn to the places of meshing, varies as the rotor progresses. Under such circumstancesl the delivery of liquid past both rotors would be unsatisfactorily pulsating. l yIt is one of the objects of this invention to make it possible to reduce these pulsations to zero; and particularly by so designing the rotor lobes that one rotor is caused to have an angular motion that cyclically accelerates and deceler- .ates, while the other rotor correspondingly has an angular motion that conversely decelerates and accelerates. The rates of acceleration of one rotor and deceleration of the other at any y instant are equal.l As a necessary requirement (Cl. 10S-126) to accomplish this, the rate of arc traverse along the pitch lines is uniform, that is, the linear velocity along the arc of the pitch line, is constant.

5 By fulfilling these requirements with elliptic `bilobar rotors that are intenneshed by teeth carried on the rotor lperipheries, smooth operation is effected and crresponding great accuracy of measurement. Due to the relation between the l angular accelerations and deceierations of the two rotors, the sum of the deliveries of liquid past the rotors remains constant, for as the delivery of one increases that of the other decreases -by like amount. There is no danger of any relative l slippage between'the rotors, since the gear teeth may be formed as accurately as desired.

It is another object of this invention to provide smoothly operating interconnected rotors for liq uid metering; and especially by ensuring that the velocity head of liquid will not materially tend to retard the normal speed of the rotors.

In thel event that bilobar rotors of this character are used for pumping, there are still other considerations involved. The motive power for such pumps almost invariably has a constant speed, or approximately a constant speed, such Ias alternating current motors or the like. If such a source of power be directly coupled to drive one of the rotors at constant speed, then obviously the other rotor rotates at a non-uniform speed, the maximum occurring when the major axis of the driving rotor is in line with the minor axis of the driven rotor; and the minimum occurring when the minor axis of the driving rotor is in line with vthe maior axis of the driven rotor. Under sich circumstances, whilen one rotor has uniform angular speed, the other has a \cyclically varia )le or pulsating angular speed,

resulting obviously in serious pulsatory discharge.

' It is accordingly anothei object of this invention to eliminate this discharge pulsatory effect,

by ensuring that both the drivin-I and driven rotors will have equal pulsatory speeds, the pulsations being in opposte directions.- Accordingly a compensating eieci is secured, and a resultant liquid delivery that is completely pulseless.

This inv intion possesses many other advan.l

tages, and.. as other objects which may 'be made more easily apparent from a consideration of sev- 5o eral embodiments of the invention. For this purpose there are shown a few forms in the ,drawings accompanying and forming part of the prescnt specification. These forms will now be deciples of the invention; but it is to be understood scribed in detail, illustrating the general printhat this detailed description is not to be taken in a limiting sense, since the scope of the invention is best defined by the appended claims.

Referring to the drawings:

Figure 1 is a longitudinal sectional view of a liquid meter embodying the invention;

Fig. 2 is an enlarged view of a quadrant of the bilobar rotor utilized in connection with the invention;

Fig. 3 is a curve explaining the manner in which the configuration of the rotor may be obtained; and

Fig. 4 is an elevation of a pump invention.

In Figure 1 a casing I is illustrated, having in this instance an inlet passageway 2 land an outlet passageway 3. Between these two passageways are the walls 4 and 5 forming internal cylindrical surfaces 6 and 1 respectively. 'I'hese cylindrical utilizing the surfaces are respectively concentric with axes 8 and 8'.

These two axes 8 and 8'4 are in parallel relation and'each of them provide axes of revolution for the shafts 9 and I0. Furthermore, these axes 3 and 8' are respectively located at the axes of symmetry of the bilobar identical or similar rotors II and I2. These vrotors are mounted securely upon the respective shafts 9 and I0 and are so arranged as to be in liquid sealing contact with the cylindrical surfaces 6 and 1 as well as with each other at the place or point where these rotors are in contact.

The rotors are of general elliptical shape; but

they depart from true elliptic configuration in a manner to behereinafter described. Considering the particular position of the rotors illustrated in Fig. 1, the major axis of the rotor I I is at this in-y stant in line with theminor axis of the rotor I2. 'Ihe flow of liquid through inlet passageway 2 exerts a torque upon the rotor I2 in a clockwise By the aid of the present invention a pulseless flow can be obtained.

As a first requirement, it is necessary so to design the rotors II and I2 that they are maintained in rolling contact with each other, without relative slippage. Accordingly it is possible then to vi'orm gear teeth I4 and I5 upon the peripheries of these rotors so that they may be in direction. At the particular instant shown, the major axis of one rotor II being alined with the minor axis of the other rotor I2, the ,ratio of the angular velocity of rotor I2 to the angular velocity of rotor vI I is equal to N, where N is the ratio of the length of the major axis to the length of the minor axis of either rotor. After a 90 revolution of the rotors from the position shown in Fig. 1, this ratio of angular velocities is equal to 1/N. c

In the process of rotation, the liquid entering through the inlet passageway 2, i's subsequently trapped in a space between each rotor and the corresponding cylindrical surface 6 or 1. At the position shown in Fig. 1, such liquid is trapped in the space I3 between the right hand side of rotor I2 and the cylindrical surface 1. 'I'his liquid is subsequently discharged through the outlet passage 3 upon a further rotation of the rotor I2. A corresponding amount .of liquid is also discharged in one-half revolution of the other rotor II, corresponding to the liquid trapped between the cylindrical wall 8 of the casing I and the left hand side of rotor II. Accordingly Ior each revolution of the rotors Il and I2, the quantity of liquid discharged through the outlet passageway 3 is approximately equal to four times the amount trapped in the space I3.

The amount of liquid delivered is accordingly quite large in comparison with the size' of the casing I. However, unless special precautions are continual meshing relationship with each other. It has been found (and it can be verified by actual lay-outs) that if the rotors II and I2 are true ellipses, the pitch lines of the gear teeth do not touch throughout a quarter revolution; they touch only at four equidistant points on each rotor. At intermediate positions the pitch lines do not touch, and accordingly the teeth mesh very badly or fall out of mesh entirely. It is possible to design by a "trial and error method in an indefinite number of different Ways so as to maintain the rotors intermeshed; but such an undefined solution does not ensure against pulsatory discharge.

In order to assure that the discharge will be free of pulsations, it is necessary that the sum of the speedsof the two rotors be constant 'for all positions of the cycle of rotation. In other words, the amount of fluid or liquid passing around rotor I I per unit of time may be reduced by any amount, provided that for the same unit of time the amount of liquid passing-around the otherl rotor I2 is increased by exactly the same amount. There will then be no resulting fluctuation in the discharge or intake rate.

The manner in which this important relationship is obtained by appropriate configuration -of the pitch line of the rotors II and I2 may be explained by reference to Figs. 2 and 3.

In Fig. 2, the pitch line Il of the upper right hand quadrant of the rotor II is illustrated. The effective major axis in this case is assumed to be 2a. Accordingly half the maior axis a is indicated by appropriate dimension. Similarly,`

half the minor axis is' given by the dimension b in that figure.

The pitch line I6 may be considered to be divided into any large number of equal arc lengths corresponding to unit arc lengths. Thus, for example, the quadrant of the pitch-line II shown has been arbitrarily divided into ten arc length units defined by the points I1 to 21 inclusive. In an actual layout, the arc length units maybe made very much shorter. The radius of the rotor between the axis 8 and the point I1 corresponds to a, half the major axis. Similarly the radius of the rotor from the axis 3 to the point 21 corl responds to b, halt the minor axis.

v arc length I1I 8 on the rotor II; rotor I2 having' interfering with the accuracy of the instrument and otherwise creating undesirable disturbances.

Now let us consider the'radius 23 extending from the axis 8 to the point'IS. When the rotor II is in such position that-the radius 23 is the one which is in alinement'with the line joining the axes 8 and 8 of Fig. 1, the rotor I2 will have moved to such a position that it has rolled on the progressed by an equal arc length. Accordingly the radiusof rotor vI2 in alinement with radius 28 corresponds to the radius 29 of Fig. 2. 'I'his radius extends from the axis 8 to the point 26, the length of the arc 28-21 corresponding to the length of the arc that corresponds to the rolling of rotor I2 on the length of the arc vI'I--I8 of rotor II.

Accordingly, the sum of the lengths of the'radii 28 and 29 must equal the distance between.the axes 8' and 8; and this in turn equals a+b.

Similarly, for this rolling relation to hold true, the sum of the length oi' the radius 30 and the length of the radius 3l must also equal the same amount, a--b. By the same reasoning the sum of the lengths of the radii 32 and 33 must also equal this same amount; and the same holdstrue of the sum of the lengths of the radii 34 and 35. The radius 36 extending to the point 22 (correspending to'the midpoint of the length of the pitch line i6) must equal half the amount a-l-b.

Thus far we have considered only the requirement that the rotors should remain in intermeshed relationship throughout their entire period of rotation. It is an additional requirement as heretofore stated that the accel-eration of angular motion of one rotor shouldbe equal to the deceleration of the angular motion of the other rotor at any instant. In this way as the rotors revolve, the acceleration of motion of rotor il asv illustrated in Fig. 1 must be matched at all times by the deceleration of the rotor I2. This acceleration continues until there is a rotation of 90 from the position of Fig. 1. Thereafter there is a deceleration inthe velocity of rotor il, and a corresponding acceleration in 'the velocity of rotor i2.

This requirement is graphically illustrated in Fig. 3. If we plot the length of radii 28 to 36 inclusive as ordinates of a curve. and if these ordinates are equally spaced along the X axis, then the curves 3l and 38 joining the ends of these ordinates must be true parabolas. These two parabolas form inverted curves smoothly joining at the 4extremity of the central radius 36. As is well known, the points on the parabola fall on a curve such that its second derivative is a constant. This second derivative then corresponds to a constant acceleration or deceleration.

course both rotors-for this purpose should be as uniformly matched -as is practicable.

In order further to assist in eliminating pulsations, divider bames 39 and 40 are placed respectively in the inlet passageway 2 and the outlet passageway 3. These bailles are placed as close as possible to the line of gear centers between the axes 8 and 8. The baffle 39 on theintake side prevents -the velocity head of the intake flow from impinging directly on the rotors Il and I2 at their point of contact. Such impingement would tend to retard their motion, since at this l pointtheir motion is directly oDpOSite to the ow of the liquid. Similarly, on the outlet side the velocity head of the outlet flow of liquid would tend to create an area of reduced back pressure at the point of contact on the outlet side. The baiile here reduces this tendency which'would again retard the motion of the rotors for the A. same reason.

The actual configuration of the pitch line curve it can then be obtained by trial and error. The parabolas 31 and 38 are first plotted, since the lengths a. and b are known and the length 36 is known, being equal to half the quantity a-i-b. Knowing these points on the two parabolas, these paraboles 31 and 38 may be plotted. Then by trial and error the configuration of the arc it can be proceeded with and it may be made as accurate as desired by repeated trials. As the rst step of this trial and error method, points 21 and i1 may be determined on the rotor li, corresponding to the minor and' major axes, as shown in Fig. 2. I'hen a triall may be made, locating pointI i8; this location is such that it corresponds to the best guess: thus, the distance between points i1 and i3 will be one-tenth of the entire length ofthe curve between points I1 and 21. A

close approximation, atleast, is possible by taking that distance i'i-i as one-tenth of the quarter periphery of a true elipse having a major axis of o and a minor axis of b. Then the point i8 is furtherdetermined by making the distance from point 3 to it equal to the line 23 on the curve of Fig. 3. Point i9 is similarly laid out, the distance between points i8 and i9 being equal to the distance between points i1 and i8, and the radius 30 being made equal in length to the line '3d of Fig. 3. If the guess at the length of the The rotation of either of the shafts 9 or l0 can be utilized to operate an indicating mechanism. This mechanism may be constructed in such a manner as not to place any appreciable load upon Y the rotation of the rotors. A

If thedevice is to be used as a gear pump, further considerations are necessary. Such a form of deivce is illustratedin Fig. 4. In this case If either of che two shafts 46- or 41 be rotated' by any conventional source of motion, serious i pulsations in the delivery would result; this occurs because such conventional sources of motion usually operate at substantially constant speed. Accordingly if either of the two shafts 46 or 41 is rotated at constant Speed, serious pulsations in the speed of the other rotor must occur.

'I'hus if the ratio of the major to the minor axis of either of the two rotors 44 and 45 be designated as N, and if we assume' that rotor 44 is the driving rotor, then obviously the ratio of transmission (or the ratio of the speed of rotor 45 with respect to the speed of rotor 44) at the instant shown is given by the amount `l/N. This corresponds to the minimum speed of rotor 45. The maximum speed occurs when the major axis of rotor 44 is in alinement with the minor axis of rotor 45. In that event the ratio of speeds of rotor 45 to rotor 44 is equal to N. Accordingly the ratio of the maximum to .the minimum speed of rotor 45 would be N2. Ordinarily, for

satisfactory purposes, the ratio N of the. major to the minor axes is chosen as neighboring the value 2. Accordingly the fluctuations vin the speed ofthe driven rotor, if the driving rotor isdriven at a uniform speed, would be such that the driven rotor would be driven four times as fast at the maximum speed its minimum speed.

In order to make it possible to equalize the fluctuations in angular velocity between the two as compared with. l

rotors and therefore provide substantially pulseless operation, the angular velocity of the driven shaft 46 is caused to vary in such a way that the ratio of the maximum to the minimum speed is equal to l\. The maximum speed of rotor 44 should occur at the instant shownin Fig. 4. This maximum angular speed is VN times the minimum speed of rotor 44 when its major axis is in alinement with the minor axis of rotor 45. If this condition is fulfilled it can readily be proved that the corresponding ratio of maximum to minimum speed of the driven rotor 45 is also equal to the VN; and there is a Aresultant substantially complete elimination in the pulsations of the liquid delivery.

In order to obtain this variation in speed of shaft 48 use ls made in this instance of a pair of bilobar driving gears 48 and 49. These gears are identical. Gear 48 is mounted on its axis of symmetry on shaft 46. The gear 49 is mounted similarly on a shaft 50 which may be -driven at a constant speed from anyconventional source of motion. These gears 48 and 49 may conveniently be placed exterior of the casing 4|. The major axis of gear 48 coincides in angular position with the major axis of rotor 44, and similarlythe major axis of the driving gear 49 isin valinement with the minor axis of the driven' gear 48. In order to obtain the required variations in speed of shaft 46, the ratio of ,the major axis to the minor axis of each of the gears 48 and 49 is made equal to V Simple mathematics l will then show that the proper speed variations are secured in connection with the rotation of the shaft 48.

'I'he bilobar elements '44, 45, 48 and 49 may be designed in accordance with the requirements set forth ln connection with the rotors Il and l2 of the form shown in Fig. 1.

What is claimed is:

l. A liquid transmission device having a casing in which there is n inlet opening and an outlet-opening, as well as a pair of similar bilobar rotors in the casing, each rotor having mutually perpendicular major and minor axes, and arranged to rotate in opposite directions about respectiveaxes of symmetry that are parallel to each other, said rotors being in continuous sealing contact with each other, and also in sealing contact with the walls of the casing, said rotors having effective radii defining by their extremities the arcuate configuration of the bilobes, said radii substantially obeying the following rule: when the arcuate configuration is divided into an integral number of equal arc lengths between the extremity of the major axis and the extremity of the minor axis, then the radii extending to the division points between the equal arc lengths, when used as ordinates uniformly spaced, have their extremities falling on a curve formed of two equal paraboli, one inverted with respect to the other, the end ordinates corresponding respectively to the major and minor axes, and the centrally located ordinate having a length corresponding to the mean between the end ordinates, the extremity of said centrally located ordinate falling on that point where the paraboli meet, and the sums of the lengths of those ordinates that are equally spaced from the end ordinates being a constant and equal to the sum of -the major and minor axes.

aseaoia rotors in the casing, each rotor having mutually perpendicular major and minor axes, and having intermeshing teeth so that they rotate in opposite directions about respective axes of symmetry that are parallel to each other, said rotors being in continuous sealing contact with each other, and also in sealing contact with the walls of the casing, said rotors having effective radii dened by the arcuate pitch line of the intermeshing teeth, and substantially obeying the following rule: when the arcuate pitch line is divided into an integral numberv of equal arc lengths between the extremity of the major axis and the extremity of the minor axis, then the radii extending to the division points between the equal arc lengths, when used as ordinates uniformly spaced, have their extremities falling on a curve formed of two equal paraboli, one inverted with respect t0 the other, the end ordinates corresponding respectively to the major and minor axes of the pitch line curve, and the centrally located ordinate having alength corresponding to the mean between the end ordinates, the extremity of said centrally located ordinate falling on that point where the paraboli meet, and the sums of the lengths of those ordinates that are equally spaced from the end ordinates being a constant and equal to the sum of the major and minor axes.

3. In a liquid transmission device, a casing having an inlet passage and an outlet passage, a pair of similar bilobar rotors within the casing, each rotor having mutually perpendicular major and minor axes, means for rotatably supporting said rotors respectively about the respective axes of symmetry, said axes being parallel to each other, and the rotors having teeth in intermeshing driving relation, and a pair of intermeshing, bilobar gears lfor driving one of Said rotors, each of said gears having mutually perpendicular major and minor axes, and rotatable about their axes of symmetry.

4. In a liquid transmission device, a casing having an inlet passage and an outlet passage, a pair of similar bilobar rotors within the casing, each rotor having mutually perpendicular major and minor axes, means for rotatably supporting said rotors respectively about the respective axes of symmetry, said axes being parallel to each other, and the rotors having teeth in intermeshing driving relation, a bilobar gear having mutually perpendicular major and minor axes, and mounted coaxially with one of said rotors and on the axis of symmetry of the gear, said gear being arranged to drive said one of said rotors, the major axis of the gear being angularly coincident with the major axis of said one of said rotors, and another gear similar to said first mentioned gear and in driving relation thereto.

5J In a liquid transmission device, a casing having an inlet passage and an outlet passage, a pair of similar bilobar rotors within the casing, each rotor having mutually perpendicular major and minor axes, means for.rotatablyisupporting said rotors respectively about the respective axes of symmetry, said axes being parallel to each other, and the rotors having teeth in intermeshing driving relation, a bilobar gear having mutually perpendicular major and minor axes, and mounted coaxially with one of said rotors and on the axis of symmetry of the gear, said gear being arranged to drive said one of said rotors, the major axis of the gear being angularly coincident with the major axis of said one of said rotors, and another gear similar to ld rst ing an inlet passage and an outlet passage, a

pair of similar bilobar rotors in said casing, each rotor having mutually perpendicular major and minor axes, means for rotatably supporting said rotors respectively about the respective axes of symmetry, said axes being parallel to each other, and the rotors having teeth in intermeshing driving relation, a bilobar gear having mutually perpendicular major and minor axes,

and mounted coaxially with one of said rotors and on the axis of symmetry of the gear, said gear being arranged to drive said one of said y rotors, the major axis of the gear being angularly coincident' with the .major axis of said one of said rotors, and another gear similar to said first mentioned gear and in driving relation thereto, the ratio of the major axis to the minor axis of each of said gears being \/N, Where N is the ratio of the major axis to the minor axis of a rotor.

" FRANCIS W. GUIBERT.

FREDERIC B. FULLER. 

